CN101109441B - Slide control device of hydrodynamic torque converter - Google Patents
Slide control device of hydrodynamic torque converter Download PDFInfo
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- CN101109441B CN101109441B CN2006100993734A CN200610099373A CN101109441B CN 101109441 B CN101109441 B CN 101109441B CN 2006100993734 A CN2006100993734 A CN 2006100993734A CN 200610099373 A CN200610099373 A CN 200610099373A CN 101109441 B CN101109441 B CN 101109441B
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Abstract
The purpose of the invention is to prevent the rapid engagement of a lock clutch when changing the engaging state of the lock clutch from sliding mode to locking mode. The invention carries out open-loop controlling over the engaging force of the lock clutch by changing the input value from slide rotary offset into the specified value in a feedback control component, so as to limit the increase rate of the engaging force (S52, S53, S55, S56) of the lock clutch when changing a hydraulic torque variator into a lock state.
Description
Technical field
The present invention relates to a kind of fluid torque converter (torque converter), particularly, relate to jointing state with lock-up clutch from the control of sliding mode when lockup state is changed.
Background technique
Be inserted into the locking control gear of the fluid torque converter in the driving force delivery system of the automatic transmission that comprises stepless speed variator, in order to reduce the deterioration of the oil consumption that causes by skidding of fluid torque converter, and in the driving zone of the impact absorption function that does not need moment of torsion increase effect and speed changer, using lock-up clutch to make between the input output key element of fluid torque converter becomes direct jointing state.Be referred to as lockdown mode, in addition, also has the bending moment pattern that will discharge fully between the input output key element and carry out the moment of torsion transmission via fluid, and to make lock-up clutch be the sliding-modes that half jointing state is kept the sliding mode of regulation, amount to 3 kinds of patterns, driving condition according to vehicle suitably switches.And the switching of this pattern is undertaken by changing locking pressure reduction, is the bending moment pattern under the situation of pressure minimum, is lockdown mode under the situation of pressure maximum.
Disclose following technology in the patent documentation 1, promptly, in such stepless speed variator, beginning to end feedback control from the state that carries out feedback control with sliding-modes, and utilize open loop control when lockdown mode is changed, by importing negative deviation forcibly, and utilize the storage effect of F/B compensator to finish locking to feedback compensator (F/B compensator).
Patent documentation 1: the spy opens the 2000-240786 communique
Summary of the invention
But, in the F/B compensator, contain under the situation of direct ratio composition (P composition), if the negative deviation of input, then the input value of compensator is with stepped variation, output value is also with stepped variation.In addition, under the situation that the F/B compensator is made of high order, the stepped variation of input value is reinforced back output.Thus, because the locking differential pressure rises sharp,, produce and impact or vibration so lock-up clutch engages rapidly.
In addition, the setting of F/B compensator is restricted because if consider to put the problems referred to above then, so in sliding-modes, be difficult to the characteristic that keeps suitable.
The objective of the invention is to, with the jointing state of lock-up clutch from sliding-modes when the lockdown mode conversion, prevent the joint rapidly of lock-up clutch.
The slide control device of fluid torque converter of the present invention has: the jointing state decision means, it is according to the driving condition of vehicle, to the sliding mode that fluid torque converter is engaged while sliding from lock-up clutch, do not slide and the conversion of the lockup state that engages is judged to lock-up clutch; The feedback control parts, its with the slip rotating deviation as input value, so that input value is 0 mode, engaging force to lock-up clutch carries out feedback control, described slip rotating deviation is the poor of slip rotating speed and the target slip rotating speed that calculates according to the driving condition of vehicle, the rotating speed of the rotating speed of the input key element that described slip rotating speed is a fluid torque converter and output key element poor; And locking controlling component, it is when fluid torque converter becomes sliding mode utilizing the feedback control parts, utilize the jointing state decision means to be judged as from sliding mode under the situation of lockup state conversion, by in the feedback control parts, input value is replaced into specified value from the slip rotating deviation, come the engaging force of lock-up clutch is carried out open loop control, to convert fluid torque converter to lockup state, and, when in the locking controlling component, the input value of feedback control parts being replaced into specified value, the increment rate of restriction engaging force.
The effect of invention
According to the present invention, owing to carry out open loop control being replaced into specified value by rotating deviation that the input value in the feedback control is promptly slided, and from sliding mode when lockup state is changed, the increment rate of the engaging force of restriction lock-up clutch, so the engaging force of lock-up clutch can sharply not increase, but gently engage.Therefore, can prevent the impact cause by engaging rapidly of lock-up clutch and the generation of vibration.
Description of drawings
Fig. 1 is the general configuration figure of the slide control device of the fluid torque converter in the expression present embodiment.
Fig. 2 is the flow chart of control of the slide control device of the fluid torque converter of expression in the present embodiment.
Fig. 3 is the corresponding diagram of the control area of expression lock-up clutch.
Fig. 4 is the chart of the relation between expression throttle valve opening and the initial stage differential pressure.
Fig. 5 is the chart that expression throttle valve opening and open loop control finish the relation between the slip rotating speed.
Fig. 6 is the chart of the relation between expression throttle valve opening and the amount of boost.
Fig. 7 is that the expression throttle valve is opened and Sliding Control finishes the chart of the relation between the slip rotating speed.
Fig. 8 is the flow chart that expression is controlled for the open loop of being carried out to the lockup state conversion from Sliding Control.
Fig. 9 is the chart of the relation between the time constant of expression throttle valve opening and low-pass filter.
The chart of the relation between the I gain when Figure 10 is expression throttle valve opening and open loop control.
Figure 11 is the chart that the expression lock-up clutch engages the relation between pressure and the lock-up clutch capacity.
Figure 12 is that the F/B compensator is the sequential chart of the situation of high order in the explanation conventional example.
Figure 13 is that the F/B compensator is the sequential chart of 1 time situation in the explanation conventional example.
Figure 14 is that the F/B compensator is the sequential chart of the situation of high order in the explanation present embodiment.
Figure 15 is the sequential chart of the situation that throttle valve opening is little among explanation Figure 14.
Figure 16 is the sequential chart of the big situation of the throttle valve opening of explanation Figure 14.
Figure 17 is that the F/B compensator is the sequential chart of 1 time situation in the explanation present embodiment.
Figure 18 is that the F/B compensator is the sequential chart of 1 time situation in the explanation present embodiment.
Embodiment
Below, with reference to accompanying drawing etc., embodiments of the present invention are at length described.Fig. 1 is the system architecture schematic representation of the slide control device of fluid torque converter of the present invention.Fluid torque converter 1 is installed between motor 14 and the speed changer 15, and the driving force of motor 14 is passed to speed changer 15 via fluid.Speed changer 15 is automatic transmission, is delivered to the driving force of speed changer 15, passes to driving wheel 16 via not shown whole speed reducer.
In fluid torque converter 1, dispose the turbine 13 that the pump impeller 12 that is connected with the output shaft of motor 14 is connected with input shaft with speed changer 15 in opposed mode.If pump impeller 12 rotations along with the rotation of motor 14, the fluid (ATF) that then is filled in fluid torque converter 1 inside flows, turbine 13 rotations thus.Fluid torque converter 1 also is built-in with the lock-up clutch 2 with turbine 13 rotations.
If lock-up clutch 2 is engaged with pump impeller 12, then the input key element of fluid torque converter 1 and output key element directly link, and fluid torque converter 1 becomes lockup state.In addition, if make input key element and output key element become half jointing state, then become the sliding mode that between input key element and output key element, produces slip.If discharge lock-up clutch 2 fully, then become the bending moment state.
Lock-up clutch 2 corresponding to the pressure differential deltap P of fluid torque converter on-load pressure (apply pressure) PA of its double side acting (below be referred to as on-load pressure PA) and fluid torque converter release pressure (release pressure) PR (below be referred to as release pressure PR) (=PA-PR) move.Lock-up clutch 2 discharges during greater than on-load pressure PA at release pressure PR, engages during less than on-load pressure PA at release pressure PR.
The engaging force of lock-up clutch 2 is that the locking capacity is determined by differential pressure Δ P.Pressure differential deltap P is big more, and the engaging force of lock-up clutch 2 is big more, and then the locking capacity is big more.Pressure differential deltap P is by 3 controls of locking control valve.
Locking control valve 3 is controlled pressure differential deltap P by control action in the on-load pressure and the release pressure of lock-up clutch 2.Act on on-load pressure PA and release pressure PR opposite to each other on locking control valve 3, and act on the pretightening force of spring 3a on the direction identical with on-load pressure PA, effect is pressed PS by locking solenoid valve 4 signal supplied on the direction identical with release pressure PR.Differential pressure Δ P is so that the mode of the pretightening force balance of these oil pressure and spring is definite.
As first pressing, the locking dutycycle D corresponding to slave controller 5 sends produces signal pressure PS to locking solenoid valve 4 with pump pressure PP.
Detect supply voltage supply voltage sensor 6, detect the rotating speed (rotating speed of the input key element of fluid torque converter) of pump impeller 12 pump impeller speed probe 7, detect the rotating speed (rotating speed of the output key element of fluid torque converter) of turbine 13 turbine speed sensor 8, detect the output shaft rotating speed of speed changer 15 transmission output speed sensor 9, detect the throttle valve opening sensor 10 of throttle valve opening and the ATF temperature transducer 11 that detects the temperature of ATF, separately checkout value is sent to controller 5.
Below, with reference to the flow chart of Fig. 2, the control of carrying out in the controller 5 is described.In addition, this control is that for example every 20ms carries out once.In addition, Sliding Control, locking control, bending moment control are respectively the control that the jointing state of lock-up clutch 2 is maintained sliding mode, lockup state, bending moment state.
In step S1, judge whether the control of fluid torque converter 1 is Sliding Control.If judge it is Sliding Control, then enter step S4, if judge it is not Sliding Control, then enter step S2.
The control of fluid torque converter 1 is with reference to corresponding diagram shown in Figure 3, retrieves according to the speed of a motor vehicle and throttle valve opening.In addition, the speed of a motor vehicle is that the constant that multiply by regulation calculates on the output shaft rotating speed of the speed changer 15 that is gone out by the transmission output speed sensor.Fig. 3 is the corresponding diagram of the expression speed of a motor vehicle, throttle valve opening and control area, under the situation of the speed of a motor vehicle less than specified value V1, makes lock-up clutch 2 be bending moment control.In addition, the speed of a motor vehicle greater than specified value V1 and situation less than specified value V2 under, be Sliding Control at throttle valve opening during less than specified value TVO1, be locking control at throttle valve opening during greater than specified value TVO1.In addition, under the situation of the speed of a motor vehicle, be locking control greater than specified value V2.
In step S2, judge whether the control of fluid torque converter 1 is locking control.If judge it is locking control, then enter step S3, if judge it is not locking control, then enter step S19.
In step S3, judge whether locking control can be transformed into complete lockup state, be the state of differential pressure command value maximum.Under situation about can change, enter step S18, under situation about cannot change, enter step S4.
In step S4, judge whether the state of a control when last time handling is bending moment control.Under the situation that is bending moment control, enter step S5, under the situation that is not bending moment control, enter step S7.Here, state of a control when judgement was last time handled is under the situation of bending moment state, owing to be the control area from the bending moment state when handling the first time of sliding mode or lockup state conversion, so in following step S5, S6, carry out the differential pressure command value being risen, to be used to carry out the preparation processing of boost action with open loop control.
In step S5, the initial stage differential pressure is set according to throttle valve opening.The initial stage differential pressure is set with reference to chart shown in Figure 4.
Among the step S6, expression is set is in the Sliding Control mark of carrying out in the boost action of utilizing open loop control (slipPTN=10).
In step S7, judge whether it is to carry out in the boost action of utilizing open loop control.Being that (slipPTN=10) under the executory situation controlled in open loop, enter step S8, not being (slipPTN ≠ 10) under the executory situation, enter step S12.
In step S8, judge whether to finish to utilize the boost action of open loop control.Finish if be judged as open loop control, then enter step S10, do not finish, then enter step S9 if be judged as open loop control.Open loop control end is judged according to following (1) formula, when (1) formula is set up, is judged as open loop control and finishes.
Nslp＜Nslp_end ……(1)
Here, Nslp is actual slip rotating speed, and Nstl_end is used for finishing rotating speed from the bending moment state to the open loop control of sliding mode conversion.Nslp_end calculates according to throttle valve opening by the chart with reference to Fig. 5.
In step S9, carry out the open loop that is used for from the bending moment state is changed to sliding mode and control.At first, by the chart of reference Fig. 6,, retrieve the amount of boost DPRS of each unit time according to throttle valve opening.Here, unit time and control cycle are of equal value, for example are 20ms.Then, according to following (2) formula, calculate differential pressure command value Pluc in the open loop control.
Pluc＝P′luc+DPRS ……(2)
Here, P ' luc is the differential pressure command value when last time handling.
On the other hand, finish, then enter step S10, finish to utilize the boost action of open loop control,, carry out the initialization process of control system in order to switch to Sliding Control if in step S8, be judged as open loop control.Initialization process is to make the integrator that uses in Sliding Control etc. corresponding with the differential pressure instruction of Sliding Control zero hour and carry out initialized processing, for example, open the method for putting down in writing in the 2000-145949 communique with the spy and carry out, omit its detailed description here.
In step S11, expression is set finishes to be used for to be in the executory Sliding Control mark of Sliding Control (SLipPTN=11) to the open loop control of sliding mode conversion from the bending moment state.
On the other hand, not to utilize in the boost action execution of open loop control, then enter step S12, judge whether it is during Sliding Control is carried out if in step S7, be judged as.If in carrying out (SLipPTN=11), then enter step S13, in carry out (SLipPTN ≠ 11), then enter step S17.
In step S13, judge whether to finish Sliding Control.Finish if be judged as Sliding Control, then enter step S15, do not finish, then enter step S14 if be judged as Sliding Control.The end of Sliding Control is judged according to following (3) formula, when (3) formula is set up, is judged as Sliding Control and finishes.
Nslp＜Nslp_SLPEND ……(3)
Here, Nslp_SLPEND is used to judge whether that the Sliding Control that can begin open loop control finishes the slip rotating speed, and this open loop control is to be used to finish Sliding Control and to the locking control transformation.Nslp_SLPEND is the chart with reference to Fig. 7, calculates according to throttle valve opening.
In step S14, carry out Sliding Control.Sliding Control is a kind of like this control, promptly, with the input value of slip rotating deviation as the F/B compensator, so that this input value is 0 mode, engaging force to lock-up clutch 2 carries out feedback control, above-mentioned slip rotating deviation is the poor of slip rotating speed and the target slip rotating speed that calculates according to the driving condition of vehicle, the rotating speed of the pump impeller 12 that above-mentioned slip rotating speed is a fluid torque converter 1 and the rotating speed of turbine 13 poor.Control system shown in Sliding Control use for example No. 3240979, No. 3183235, No. 3230465 patents etc. is carried out, and calculates desired differential pressure command value, omits its detailed description here.
On the other hand, if in step S13, be judged as Sliding Control and finish, then enter step S15, the control system that is used to switch to open loop control is carried out initialization process, this open loop control is used to finish Sliding Control and changes to lockup state.
In step S16, the Sliding Control mark (SlipPTN=12) that expression is used for being in to the boost action lockup state conversion, that utilize open loop control from Sliding Control enforcement is set.
In step S17, carry out the open loop that is used for from Sliding Control is changed to lockup state and control.Open loop control is a kind of like this control, that is, be replaced into the steady state value of regulation by the input value with F/B compensator in the Sliding Control from the slip rotating deviation, and the engaging force of lock-up clutch is carried out open loop control, makes it be transformed into lockup state.In addition, the back describes in detail the control of the open loop in this step.
On the other hand, finish if be judged as locking among the step S3, then because the joint action of locking control is finished, so enter step S18, P remains maximum pressure with the differential pressure Δ.
Not lockup state if be judged as among the step S2, then owing to be that so enter step S19, P remains minimum pressure with the differential pressure Δ in the bending moment control.At this moment, between the minimum pressure of differential pressure command value and differential pressure Δ P, exist under the situation of difference, in command value, produce the mode of ladder difference so that command value can not become minimum pressure rapidly, command value is gradually changed with the variance ratio of regulation.
Then, with reference to the flow chart of Fig. 8, explain the open loop control of being carried out to the lockup state conversion from Sliding Control in step S17.
In step S50, realize open loop control for employed F/B compensator in the Sliding Control of the step S14 that uses Fig. 1, calculating and forcing the input value of the F/B compensator set is deviation Err.Deviation Err is the negative deviation of setting according to throttle valve opening, opens the record of 2000-240786 communique according to the spy and calculates, and omits its detailed description here.
In step S51, judge that the F/B compensator is to be made of 1 time PI controller, still by constituting more than or equal to 2 times high order PI controller.If 1 time, then enter step S55, if high order then enters step S52.The judgement of F/B compensator can be carried out like this,, uses the formation sign FB_TYPE of F/B compensator that is, and the situation of FB_TYPE=0 as 1 PI controller, as the high order controller, is judged whether it is FB_TYPE=0 with the situation of FB_TYPE ≠ 0.
At the F/B compensator is under the situation about constituting of the controller by high order, if the deviation Err that sets among the step S50 is directly imported, then the input value of F/B compensator is with stepped variation, the output value of stepped variation has been strengthened in output thus, so, in following step S52～S54, carry out the processing of the variance ratio of restriction input value in order to prevent this situation.
In step S52, the time constant TErr of compute low pass filtered device (following table is shown LPF).Time constant TErr is by with reference to chart shown in Figure 9, according to throttle valve opening, calculates in the throttle valve opening mode that large time constant is more little more.
In step S53, the LPF to deviation Err implements to have time constant TErr calculates the Lfil_Err with 1 delay.
Here, deviation Err is the value of setting according to throttle valve opening, and the variation of this deviation Err is by constituting of the sine wave with different frequency composition.Wherein, utilize LPF and the sine wave with the following frequency content of assigned frequency is passed through, obtain relative deviation Err by combination and have the value that postpones for 1 time.In addition, the time constant TErr of LPF is big more, and it is just long more in order to reach the needed time of deviation Err to have the value that postpones for 1 time.
In step S54, the input value Fbin of F/B compensator is set at the Lfil_Err that calculates among the step S53.
Under the situation that the F/B compensator is made of 1 time PI controller, if the deviation Err that sets among the step S50 is directly imported, then the input value of F/B compensator is with stepped variation, the output value that is directly proportional with it is also with stepped variation thus, so, in order to prevent this situation, in following step S55～S57, carry out the processing of the variance ratio of restriction output value.
In step S55, be that the P composition is set at 0 with the direct ratio composition of PI controller.
In step S56, by with reference to chart shown in Figure 10, according to throttle valve opening, in big more its big more mode of throttle valve opening, the integration composition of setting the PI controller is I composition (I gain).
In step S57, the input value Fbin of F/B compensator is set at deviation Err.
In step S58, Fbin is imported the F/B compensator, calculate the output value FBout of F/B compensator.The output value FBout of F/B compensator opens the disclosed method of 2000-240786 communique by the spy and calculates, and omits its detailed description here.
At step S59, according to the output value FBout of F/B compensator, calculate the locking capacity, by with reference to chart shown in Figure 11, calculate in order to realize the needed differential pressure command value of locking capacity.The locking capacity is calculated by No. 3240979, No. 3230465 disclosed methods of patent, omits its detailed description here.
Comprehensive above-mentioned control with reference to the sequential chart of Figure 12～Figure 18, illustrates the effect of present embodiment.
At first, use Figure 12, Figure 13 that conventional example is described.Figure 12 is that the F/B compensator is the sequential chart of the situation of high order in the conventional example.(a) expression throttle valve opening, (b) expression F/B compensator input value, (c) expression F/B compensator output value, (d) expression differential pressure command value, (e) expression engine speed, (f) expression initial speed (speed changer input speed).
At moment t1, to being used for the open loop control transformation that locking engages, the input value of F/B compensator is with the stepped difference Err that is changed to from Sliding Control for control range.Thus, the output value of F/B compensator changes in the mode of strengthening stepped variation, and the differential pressure command value sharply rises.Therefore, engine speed sharply reduces, become to equate with initial speed, afterwards, engine speed and initial speed vibration.
Figure 13 is that the F/B compensator in the conventional example is the sequential chart of 1 time situation.(a) expression throttle valve opening, (b) expression F/B compensator input value, (c) expression P gain, (d) expression F/B compensator output value, (e) expression differential pressure command value, (f) expression engine speed, (g) expression initial speed.
At moment t1, to being used for the open loop control transformation that locking engages, the input value of F/B compensator is with the stepped deviation Err that is changed to from Sliding Control in the control area.Owing to comprise the direct ratio composition in the F/B compensator, with stepped variation, the differential pressure command value is with stepped rising so the output value of F/B compensator is directly proportional with input value.Therefore, engine speed sharply descends, while engine speed is vibrated and restrained to initial speed afterwards.
Then, with reference to Figure 14～Figure 18 present embodiment is described.Figure 14 is the sequential chart that F/B compensator of the present invention is the situation of high order, implements the effect that LPF produces among the step S53 of the flow chart of presentation graphs 8.(a) expression throttle valve opening, (b) expression F/B compensator input value, (c) expression F/B compensator output value, (d) expression differential pressure command value, (e) expression engine speed, (f) expression initial speed.In addition, the dotted line among the figure is represented conventional example.
At moment t1, if the control area from Sliding Control to being used for the open loop control transformation that locking engages, then the value Lfil_Err that will implement to export behind the LPF to the setting value Err of the input deviation of F/B compensator is as F/B compensator input value.Because by this filtering operation, the input value of F/B compensator changes smoothly, so the output value of F/B compensator also changes smoothly.Thus, because the also rising gradually of differential pressure command value, so engine speed is reduced to initial speed gradually.
Figure 15, Figure 16 are the sequential charts that F/B compensator of the present invention is the situation of high order, are illustrated among the step S52 of flow chart of Fig. 8, set the effect that time constant TErr produced of LPF corresponding to the aperture of throttle valve.Figure 15 is the little situation of throttle valve opening, and Figure 16 is the big situation of throttle valve opening, (a) expression F/B compensator input value separately, (b) expression F/B compensator output value, (c) expression engine speed, (d) expression initial speed, (e) the expression speed of a motor vehicle.
At moment t1, if the control area from Sliding Control to being used for the aperture control transformation that locking engages, then set the time constant TErr of LPF.Among Figure 15, because throttle valve opening is little, so set time constant TErr bigger.Because under the little low speed of a motor vehicle of throttle valve, low speed state, be easy to generate impact by the joint rapidly of lock-up clutch 2, thus bigger by time constant TErr is obtained, can realize that level and smooth locking engages.
Among Figure 16, so because throttle valve opening is set time constant TErr less greatly.Because under the state of the big higher speed of a motor vehicle of throttle valve opening, higher rotation speed, joint rapidly by lock-up clutch 2 is not easy to produce impact, in addition, if spended time on locking engages, then the durability of the surfacing of lock-up clutch 2 reduces, so, by setting time constant less, and realize that apace locking engages.
Figure 17 is the sequential chart that F/B compensator of the present invention is 1 time a situation, and among the step S55 of the flow chart of presentation graphs 8, the P composition of the F/B compensator that will be made of PI control is set at 0 effect that produces.(a) expression throttle valve opening, (b) expression F/B compensator input value, (c) expression P gain, (d) expression F/B compensator output value, (e) expression differential pressure command value, (f) expression engine speed, (g) expression initial speed.In addition, the dotted line among the figure represents that the P gain is not set to 0 situation.
At moment t1, if the control area from Sliding Control to being used for the open loop control transformation that locking engages, then the P gain setting with the F/B compensator is 0.Therefore, though the input value of F/B compensator with stepped variation, output value is not directly proportional with input value yet, but changes smoothly.Therefore, because the also rising gradually of differential pressure command value, so engine speed is reduced to initial speed gradually.
Figure 18 is the sequential chart that F/B compensator of the present invention is 1 time a situation, among the step S55 of the flow chart of presentation graphs 8, the P composition of the F/B compensator that will be made of the PI controller is set at 0, sets the effect that I becomes branch to produce corresponding to throttle valve opening simultaneously in step S56.(a) expression throttle valve opening, (b) expression F/B compensator input value, (c) expression P gain, (d) expression I gain, (e) expression F/B compensator output value, (f) expression differential pressure command value, (g) expression engine speed, (h) expression initial speed.In addition, dotted line represents not make the I gain to depend on the situation of throttle valve opening among the figure.
At moment t1, if the control area from Sliding Control to being used for the open loop control transformation that locking engages, then the P gain setting with the F/B compensator is 0, sets the I gain corresponding to throttle valve opening simultaneously.In addition, if at moment t2, it is big that depress throttle pedal and throttle valve opening become, and then the input value of F/B compensator increases.But, because the P composition is 0, thus big even the input value of F/B compensator becomes, sharply not becoming big mode with output value yet, engine speed rises.
Therefore, cooperate throttle valve opening increase and must be bigger with the I gain setting.Thereby because the climbing of the output value of F/B compensator uprises, the climbing of differential pressure command value also uprises, so can suppress the useless rising of engine speed.
As mentioned above, in the present embodiment, be replaced into specified value from the slip rotating deviation by input value with the F/B compensator, though from Sliding Control to the locking control transformation, also can suppress the rapid rising of the output value of F/B compensator.Thus, when realizing the rapid joint of lock-up clutch 2, the rapid rising of the differential pressure command value that calculates according to output value can also be prevented, thereby the impact that produces by engaging rapidly of lock-up clutch 2 or the generation of vibration can be prevented.
In addition and since with the input value of F/B compensator when the slip rotating deviation is replaced into specified value, input value is had lingeringly changes to specified value from the slip rotating deviation, so the input value of F/B compensator can rapid change, output value is smooth variation also.Thus, prevent the rapid rising of the differential pressure command value that calculates according to output value, can prevent the impact that produces by engaging rapidly of lock-up clutch 2 and the generation of vibration.
In addition, the change delay of input value is set in big more its more little mode of throttle valve opening.Thus,, prevent the joint rapidly of lock-up clutch 2 so the differential pressure command value rises gently, prevent to follow the impact of locking joint or the generation of vibration because a throttle valve opening hour delay is set greatlyyer.Owing to set lessly late at the throttle valve opening long time delay, so carry out the joint of lock-up clutch 2 apace, can prevent reduction, can prevent that the invalid rotation of motor 14 from rising simultaneously by the durability of the surfacing that continues the sliding mode generation for a long time.
In addition, with the input value of F/B compensator when the slip rotating deviation is replaced into specified value, because by will implementing the value Lfill_Err input F/B compensator that obtains behind the LPF to deviation Err, the input value of F/B compensator can rapid change, so yet smooth variation of output value.Thus, the rapid rising of the differential pressure command value that calculates according to output value can be prevented, and then the impact that the joint by lock-up clutch 2 produces or the generation of vibration can be prevented.
In addition, set the time constant TErr of LPF in big more its more little mode of throttle valve opening.Thus, because throttle valve opening hour, time constant TErr sets greatlyyer, so the differential pressure command value rises gently, can prevent the joint rapidly of lock-up clutch 2, the impact that prevents to follow locking to engage and produce or the generation of vibration.Because when throttle valve opening is big, time constant is set lessly, so carry out the joint of lock-up clutch 2 apace, can prevent decline by the durability of the surfacing that continues the sliding mode generation for a long time, prevent that simultaneously the useless rotation of motor 14 from rising.
In addition, when the F/B compensator is made of the PI controller, by the P composition is set at 0, sharply rise even be input to the deviation Err of F/B compensator, output value is not proportional but gently change with input value yet.Thus, prevent the rapid rising of the differential pressure command value that calculates according to output value, thereby can prevent the impact that the rapid joint by lock-up clutch 2 produces and the generation of vibration.
In addition, when the F/B compensator is made of the PI controller, the P composition is set at 0, sets the I composition in big more its big more mode of throttle valve opening simultaneously.Thus, because at depress throttle pedal and throttle valve opening when increasing, the I composition also increases accordingly, so even the P composition is set at 0, also can make the differential pressure command value rise to desired value, lock-up clutch 2 can be engaged apace, the decline of the durability of the useless rotation rising of the motor 14 that causes by the delay that engages and surfacing can be prevented simultaneously.By hour reducing the I composition, prevent the rapid rising of differential pressure command value, thereby can prevent the impact that causes by engaging rapidly of lock-up clutch 2 or the generation of vibration at throttle valve opening.
Obviously, the present invention is not limited to the mode of execution of above explanation, also can carry out all distortion or change in the scope of this technological thought, and they also are equal to the present invention.
Claims (7)
1. vehicle that is equipped with fluid torque converter is characterized in that possessing:
Fluid torque converter, it transmits the driving force of motor via fluid, and has lock-up clutch;
The jointing state decision means, it is according to the driving condition of vehicle, while the sliding mode to making described fluid torque converter slide and engage from described lock-up clutch does not slide and the conversion of the lockup state that engages is judged to described lock-up clutch;
The feedback control parts, its with the slip rotating deviation as input value, so that described input value is 0 mode, engaging force to described lock-up clutch carries out feedback control, described slip rotating deviation is the poor of slip rotating speed and the target slip rotating speed that calculates according to the driving condition of vehicle, the rotating speed of the rotating speed of the input key element that described slip rotating speed is described fluid torque converter and output key element poor;
The locking controlling component, it is when described fluid torque converter becomes described sliding mode utilizing described feedback control parts, utilize described jointing state decision means to be judged as from described sliding mode under the situation of described lockup state conversion, by in described feedback control parts, described input value is replaced into specified value from the slip rotating deviation, come the engaging force of described lock-up clutch is carried out open loop control, to convert described fluid torque converter to described lockup state; And
The engaging force limiting part when it is replaced into described specified value in the described input value of utilizing described locking controlling component with described feedback control parts, limits the increment rate of described engaging force.
2. the vehicle that is equipped with fluid torque converter as claimed in claim 1 is characterized in that,
Described engaging force limiting part changes to described specified value by described input value is had lingeringly from described slip rotating deviation when described input value is replaced into described specified value, limit the increment rate of described engaging force.
3. the vehicle that is equipped with fluid torque converter as claimed in claim 2 is characterized in that,
Also have the throttle valve opening detection part, its detection is used to regulate the aperture of the throttle valve of described air input of engine by air,
Described delay is set in big more its more little mode of described throttle valve opening.
4. the vehicle that is equipped with fluid torque converter as claimed in claim 2 is characterized in that,
Described engaging force limiting part by described input value being replaced as to the value behind the described specified value enforcement lower pass-filter, changes to described specified value and described input value is had lingeringly from described slip rotating deviation.
5. the vehicle that is equipped with fluid torque converter as claimed in claim 4 is characterized in that,
The time constant of described low-pass filter is big more with described throttle valve opening, and its more little mode is set.
6. the vehicle that is equipped with fluid torque converter as claimed in claim 1 is characterized in that,
Described feedback control parts are made of the PI controller,
Described engaging force limiting part is set at 0 by the direct ratio composition with described PI controller, limits the increment rate of described engaging force.
7. the vehicle that is equipped with fluid torque converter as claimed in claim 6 is characterized in that,
Also have the throttle valve opening detection part, its detection is used to regulate the aperture of the throttle valve of described air input of engine by air,
Described engaging force controlling component is set at 0 with the direct ratio composition of described PI controller, sets the integration composition in big more its big more mode of described throttle valve opening simultaneously, thus, limits the increment rate of described engaging force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2006100993734A CN101109441B (en) | 2006-07-19 | 2006-07-19 | Slide control device of hydrodynamic torque converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2006100993734A CN101109441B (en) | 2006-07-19 | 2006-07-19 | Slide control device of hydrodynamic torque converter |
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| Publication Number | Publication Date |
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| CN101109441A CN101109441A (en) | 2008-01-23 |
| CN101109441B true CN101109441B (en) | 2010-08-11 |
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| CN2006100993734A Expired - Fee Related CN101109441B (en) | 2006-07-19 | 2006-07-19 | Slide control device of hydrodynamic torque converter |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| US9303701B2 (en) * | 2014-07-16 | 2016-04-05 | Ford Global Technologies, Llc | Method of controlling a transmission having an impeller clutch |
| US9988038B2 (en) * | 2015-04-09 | 2018-06-05 | Ford Global Technologies, Llc | Methods and system for controlling torque flow through a torque converter |
| BE1025861B9 (en) * | 2017-12-29 | 2019-10-14 | Punch Powertrain Nv | DRIVER FOR A COUPLING IN A DRIVE LINE AND METHOD FOR DRIVING A COUPLING IN A DRIVE LINE AND A DRIVE LINE CONTAINING THE DRIVING DEVICE |
| CN115217928B (en) * | 2022-02-07 | 2023-11-10 | 广州汽车集团股份有限公司 | Control method and device applied to hydraulic torque converter in equipment and storage medium |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1521430A (en) * | 2003-02-13 | 2004-08-18 | �ղ��Զ�����ʽ���� | Lockup control of torque converter |
| CN1616854A (en) * | 2003-11-12 | 2005-05-18 | 日产自动车株式会社 | Power transmission device and lockup control method for torque converter |
| CN1629520A (en) * | 2003-12-18 | 2005-06-22 | 日产自动车株式会社 | Lockup control apparatus and method for vehicular torque converter |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1521430A (en) * | 2003-02-13 | 2004-08-18 | �ղ��Զ�����ʽ���� | Lockup control of torque converter |
| CN1616854A (en) * | 2003-11-12 | 2005-05-18 | 日产自动车株式会社 | Power transmission device and lockup control method for torque converter |
| CN1629520A (en) * | 2003-12-18 | 2005-06-22 | 日产自动车株式会社 | Lockup control apparatus and method for vehicular torque converter |
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